EP1301691A1 - Control of an electromagnetic steering valve of a camshaft phaser - Google Patents
Control of an electromagnetic steering valve of a camshaft phaserInfo
- Publication number
- EP1301691A1 EP1301691A1 EP01945701A EP01945701A EP1301691A1 EP 1301691 A1 EP1301691 A1 EP 1301691A1 EP 01945701 A EP01945701 A EP 01945701A EP 01945701 A EP01945701 A EP 01945701A EP 1301691 A1 EP1301691 A1 EP 1301691A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- spool
- movable valve
- control valve
- controller
- hydraulic pressure
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/34403—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using helically teethed sleeve or gear moving axially between crankshaft and camshaft
- F01L1/34406—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using helically teethed sleeve or gear moving axially between crankshaft and camshaft the helically teethed sleeve being located in the camshaft driving pulley
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
- F01L2001/34423—Details relating to the hydraulic feeding circuit
- F01L2001/34426—Oil control valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L2800/00—Methods of operation using a variable valve timing mechanism
Definitions
- the present invention generally relates to a movable valve apparatus for an internal combustion engine. More specifically, the present invention relates to a movable valve apparatus for an internal combustion engine having a movable valve mechanism that changes the working condition of the air intake valve or exhaust valve depending on a supplied hydraulic pressure of the working fluid.
- Japanese Laid-Open Patent Application H8-28219 discloses a movable valve mechanism that changes an opening/closing timing of an air intake or exhaust valve according to a supplied hydraulic pressure of working fluid.
- the hydraulic pressure supplied to this movable valve mechanism is adjusted according to a working condition of a spool that reciprocates within a sleeve of a hydraulic pressure control valve.
- the hydraulic pressure control valve includes a return spring that always biases the spool to a minus side, and a solenoid that drives the spool to the other side in response to an input of a control signal.
- valve lock When a foreign object (impurity) such as chips that entered the working fluid during chip processing becomes jammed inside the hydraulic pressure control valve, particularly at a partition portion between a drain port formed in the sleeve and the spool, so-called valve lock may occur. Therefore, in the above-mentioned patent application, when it is determined that a foreign object is jammed, more specifically when an actual cam phase detected by a cam angle sensor and a target cam phase obtained by a separate calculation differ by more than a predetermined value, a foreign object removal operation is executed, during which the spool reciprocates temporarily.
- Jn a valve timing adjustment apparatus disclosed in Japanese Laid-Open Patent Application H9-195805 the foreign object removal operation is executed when the hydraulic pressure control valve keeps an opening that is below a predetermined opening for longer than a predetermined period of time, when the engine is started or stopped, or while the engine is idling.
- Application H8-28219 which proposes executing the foreign object removal operation when a foreign object is actually jammed, that the targeted valve timing may not be achieved temporarily due to the foreign object removal operation, depending on the working condition of the spool at the time the foreign object removal operation is executed. Accordingly, malfunctioning such as insufficient acceleration and unstable idling may result.
- an example of a movable valve mechanism is described in Japanese Laid-Open Patent Application H7-180514.
- This Japanese application describes a movable valve mechanism in which a phase of a camshaft of the air intake valve or the exhaust valve is changed relative to a crankshaft by a controller.
- the controller of this application operates a cam switching mechanism that switches a plurality of cams, and a mechanism that changes a working angle of the air intake valve (valve lift amount).
- an engine control unit has a memory or CPU that is preferably utilized to stores and executes various engine controls such as the aforementioned driving control of the spool, various controls of fuel injection period, fuel injection amount, and igniting timing.
- a port for supplying hydraulic pressure to the movable valve mechanism a port for introducing the hydraulic pressure from the hydraulic pressure source, and a plurality of ports for draining are formed in the sleeve of the aforementioned ' hydraulic pressure control valve. These ports are selectively closed and opened based on the position of the spool, in order to adjust the supply of hydraulic pressure to the movable valve mechanism.
- a movable valve apparatus for adjusting an air control valve of an internal combustion engine.
- the movable valve apparatus basically comprises a movable valve mechanism, a hydraulic pressure control valve and a controller.
- the movable valve mechanism is operatively controlled by hydraulic pressure of a working fluid to adjusting the air control valve.
- the hydraulic pressure control valve is operatively coupled to the movable valve mechanism to adjust the hydraulic pressure of the working fluid supplied to the movable valve mechanism.
- the hydraulic pressure control valve includes a spool reciprocally coupled within a sleeve to control the hydraulic pressure of the working fluid supplied to the movable valve mechanism.
- the controller is operatively coupled to the hydraulic pressure control valve to drive and control the spool within the sleeve.
- the controller is configured to execute a foreign object removal operation upon the controller determining that the spool is in a returning state in which the spool starts moving toward an initial position.
- the spool is temporarily reciprocated by the controller to remove foreign objects inside the hydraulic pressure control valve during the foreign object removal operation.
- Figure 1 is a cross sectional view of the movable valve apparatus for internal combustion engine in accordance with the embodiment of the present invention, corresponding to a state in which the spool is maintained in the initial position;
- Figure 2 a cross sectional view in accordance with the aforementioned embodiment, corresponding to a state in which the spool is maintained at a farthest position from the initial position;
- Figure 3 a cross sectional view in accordance with the aforementioned embodiment, corresponding to a state in which the spool is maintained at an intermediate position;
- Figure 4 a characteristics chart showing the flow of the control in accordance with the present embodiment.
- Figure 5 a flowchart showing a flow of control where the returning state is determined based on a change in the throttle opening and a switch of idle switch.
- a movable valve apparatus 1 for an internal combustion engine is illustrated to explain a first embodiment of the present invention.
- the movable valve apparatus 1 is illustrated as applied to an air intake valve of the internal combustion engine.
- air control valve refers to either an air intake valve or an air exhaust valve.
- the movable valve apparatus 1 basically includes a movable valve mechanism 10, a hydraulic pressure control valve 12 and a controller 14.
- the movable valve mechanism 10 changes the opening/closing timing of an air intake valve (not shown in the Figures) in accordance with the hydraulic pressure of working fluid being supplied thereto.
- the hydraulic pressure control valve 12 adjusts the hydraulic pressure supplied to the movable valve mechanism 10.
- the controller 14 drives and controls the hydraulic pressure control valve 12.
- the controller 14 indirectly drives and controls the movable valve mechanism 10 as explained below in more detail.
- the movable valve mechanism 10 is fixed to a front end of a camshaft 16 via a hollow bolt 18.
- the camshaft 16 drives the air intake valve in a conventional manner.
- the movable valve mechanism 10 basically includes an axle portion 20, an outer tubular portion 24, and a piston 26.
- the axle portion 20 rotates together with the camshaft 16.
- the outer tubular portion 24 is integrally formed on an inner peripheral side of a cam sprocket or a cam pulley 22.
- the cam sprocket or cam pulley 22 receives rotational power from the crankshaft (not shown) via a chain or a belt (not shown) in a conventional manner.
- the outer tubular portion 24 rotates in sync with the crankshaft.
- the piston 26 has a ring shape and meshes with an outer peripheral surface of the axle portion 20 and an inner peripheral surface of the outer tubular portion 24.
- the piston 26 is preferably constructed as two members or parts 26a and 26b in order to prevent a backlash.
- the members 26a and 26b are biased in directions toward and away from each other by a spring not shown in the Figures.
- First and second helical splines are formed by the meshing portions 27 at the inner and outer peripheral surfaces of the piston 26, respectively.
- the first helical spline mates with a corresponding helical spline formed on an outer peripheral surface of the axle portion 20, while the second helical spline mates with a corresponding helical spline formed on an inner peripheral surface of the outer tubular portion 24.
- a first hydraulic pressure chamber 29 is formed which shall be referred to as the "delayed angle chamber”.
- a second hydraulic pressure chamber 32 is formed which shall be referred to as the "advanced angle chamber”.
- the delayed angle chamber 29 and the advanced angle chamber 32 are both basically defined by an inner peripheral surface of the outer tubular portion 24, the axial ends of the piston 26, and end covers 28a and 28b.
- the working fluid is supplied to the hydraulic pressure chamber 29 through a first fluid path 34 and to the hydraulic pressure chamber 32 through a second fluid path 36.
- the first and second fluid paths 34 and 36 are formed in inner portions of the camshaft 16 and the bolt 18.
- the piston 26 moves in an axial direction (the left and right direction in Figures 1- 3), in response to the hydraulic pressure in the hydraulic chambers 29 and 32.
- This axial movement of the piston 26 is converted into a relative rotational movement between the axle portion 20 and the outer tubular portion 24 via the aforementioned helical splines. Accordingly, the rotational phases of the members 20 and 24 change continuously.
- a change in the rotational angle of the cam sprocket 22 changes the rotational angle of the camshaft 16 relative to the rotational angle of the cam sprocket' 22 changes. Therefore, the opening/closing timing (valve timing) of the air intake valve changes continuously.
- the movable valve mechanism 10 is compact and easy to install in the engine.
- the movable valve mechanism 10 is also advantageous in that a low number of members or parts are utilized.
- the hydraulic pressure control valve 12 selectively opens and closes the aforementioned first and second fluid paths 34 and 36, based on an ON-OFF drive (duty control) operated by a control signal from the controller 14. In this manner, the stopping position of the piston 26 is changed as needed and/or desired.
- the hydraulic pressure control valve 12 includes a tubular sleeve 38, a spool 40, a return spring 42, and a solenoid 44.
- the spool 40 reciprocates within the tubular sleeve 38.
- the return spring 42 functions as biasing means for biasing the spool 40 toward an initial position (left-hand side in the Figures 1-3).
- the solenoid 44 drives the spool 40 in response to a control signal from the controller 14, and moves the spool 40 in a direction away from the initial position against the urging force of the return spring 42.
- the sleeve 38 has a plurality of ports formed therein. The ports are opened and closed depending on an axial position of the spool 40.
- the sleeve 38 includes a first port 34a that connects to the first fluid path 34, a second port 36a that connects to the second fluid path 36, a hydraulic pressure introduction port 46a, and a series of drain ports 48a.
- Working fluid is introduced into the hydraulic pressure introduction port 46a from a hydraulic pressure pump 46, which is a hydraulic pressure source.
- the series of drain ports 48a are connected to an oil pan 48 in a conventional manner.
- the opening/closing timing of the air intake valve is set to the most delayed angle side to achieve a delayed angle. Also, when the engine is stopped and the supplied hydrauhc pressure is reduced, the camshaft 16 is maintained at the most delayed angle side, which is the initial state, due to a valve reactionary force that is applied to the camshaft 16.
- the spool 40 when the supplied electric current (or electric voltage) to the solenoid 44 is at an intermediate level, in other words when the aforementioned duty level is about 50%, the spool 40 is maintained at an intermediate position as shown in Figure 3. In this case, the spool 40 closes both the first port 34a and the second port 36a. hi this manner, the hydrauhc pressures in the first and second hydrauhc pressure chambers 29 and 32 are maintained (locked). Accordingly, the piston 26 remains in its position.
- the controller 14 is an engine control unit that preferably includes a microcomputer (CPU) and/or a memory device with a control program that drives and controls the spool 40 by outputting a control signal (duty signal) to the solenoid 44 of the hydrauhc pressure control valve 12.
- the controller 14 can also include other conventional, components such as an input interface circuit, an output interface circuit, and storage devices such as a ROM (Read Only Memory) device and a RAM (Random Access Memory) device.
- the controller 14 is operatively coupled to the solenoid 44 in a conventional manner.
- the spool 40 is driven and controlled in the manner described above, based on working conditions of the engine such as engine rotations, load, water temperature, and vehicle speed, which are detected by each sensor.
- the memory or CPU stores and processes various engine controls such as fail-safe, adjustment of igniting timing, fueling timing, and fuel supply amount, and over-supply adjustment. It will be apparent to those skiUed in the art from this disclosure that the precise structure and algorithms for the controller 14 can be any combination of hardware and software that will carry out the functions of the present invention. In other words, "means plus function" clauses as utilized in the specification and claims should include any structure or hardware and/or algorithm or software that can be utilized to carry out the function of the "means plus function” clause.
- the control target angle is a target value of the transmitted angle of the camshaft 16 relative to rotational angle of the crankshaft. Accordingly, the control target angle corresponds to a target value of the opening/closing timing of the air intake valve. Based on the working condition of the engine, this control target angle is sequentially determined by the controller 14.
- the duty ratio is switched from 0% to 100% as seen in part (a) of the graph shown in Figure 4. Accordingly, as seen in part (b) of the graph shown in Figure 4, the spool 40 moves from the most delayed angle side, which is the initial position, to the advanced angle side. In this manner, the actual transmitted angle proceeds with some delay in response, as seen in part (d) of the graph shown in Figure 4. Once it is determined that this transmitted angle reaches the control target angle, the aforementioned duty ratio is switched to 50%. Accordingly, the spool 40 is maintained at the intermediate position as shown in Figure 3. Therefore, the actual transmitted angle remains in the predetermined advanced angle state.
- the control target angle changes to the most delayed angle side from an advanced angle state (corresponding to the timing T2)
- the foreign object removal operation is executed by making the spool 40 temporarily reciprocate in an axial direction to remove foreign objects from the hydrauhc pressure control valve 12.
- the duty ratio is switched back and forth between 0% and 100% at a predetermined cycle during a predetermined period ⁇ T.
- This reciprocating cycle of the foreign object removal operation is set sufficiently shorter than the response time of the movable valve mechanism 10, such that the opening/closing timing of the air intake valve (actual transmitted angle) does not change inadvertently.
- the reciprocating cycle can be set as 10Hz for 0.1 sec.
- the foreign object removal operation is executed when it is determined that the spool 40 is in the returning state, in which the spool 40 starts moving toward the initial position on the delayed angle side. Therefore, precipitation, accumulation, and jamming of foreign objects within the hydrauhc pressure control valve 12 are prevented. Accordingly, the jamming of foreign object at the time the spool 40 returns to the delayed angle side is prevented securely. Therefore, it is possible to avoid undesirable situations in which the opening/closing timing of the air intake valve cannot return to the initial state on the delayed angle side because the spool 40 cannot return to its initial position due to such jamming of the foreign object.
- the opening closing timing of the air intake valve may not temporarily achieve the target value due to the jamming of the foreign object.
- the jamming of the foreign object can be automatically resolved when the spool 40 returns to the initial position due to the spring force of the return spring 42.
- the aforementioned foreign object removal operation is executed. Therefore, the spool 40 can surely return to the initial position. Furthermore, by limiting the conditions under which the foreign object removal operation is executed to when the spool is in the returning state, it is possible to limit negative effects such as a decrease in responsiveness and an increase in power consumption that occur due to the execution of the foreign object removal operation to the minimum level.
- the foreign object removal operation is executed regardless of whether a foreign object is actually jammed. Therefore, there is no need to provide a sensor device for detecting jamming of a foreign object. Accordingly, it is possible to reduce the number of members, and simplify the apparatus. Furthermore, since the returning state of the spool 40 is determined based on the decrease in the control target angle (change to the delayed angle side), there is no need for a separate sensor device to determine the returning state. Accordingly, it is possible to simplify the apparatus.
- FIG. 5 shows a flow chart of the control by the controller 14 in which the returning state is determined based on a change in the idle switch and a change in the throttle opening.
- step SI the throttle opening is detected. Jf the throttle opening decreases by more than a predetermined amount (step S2), or if the idle switch is switched from the OFF side to the ON side (step S3), the returning state is determined. Accordingly, the controller 14 proceeds to step S4, and executes the foreign object removal operation.
- the movable valve mechanism 10 is of a type that changes the opening/closing timing (phase) of the air intake valve.
- the movable valve mechanism 10 can be of a type that switches between a plurality of cams having different valve lift amounts. In that case, it is configured such that a cam having a small valve lift amount is selected when the spool 40 of the hydrauhc pressure control valve 12 is in the initial position.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
Abstract
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2000220391A JP2002030910A (en) | 2000-07-21 | 2000-07-21 | Variable valve system of internal combustion engine |
JP2000220391 | 2000-07-21 | ||
PCT/JP2001/005619 WO2002008578A1 (en) | 2000-07-21 | 2001-06-28 | Control of an electromagnetic steering valve of a camshaft phaser |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1301691A1 true EP1301691A1 (en) | 2003-04-16 |
EP1301691B1 EP1301691B1 (en) | 2006-04-19 |
Family
ID=18715006
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP01945701A Expired - Lifetime EP1301691B1 (en) | 2000-07-21 | 2001-06-28 | Control of an electromagnetic steering valve of a camshaft phaser |
Country Status (7)
Country | Link |
---|---|
US (1) | US6615779B2 (en) |
EP (1) | EP1301691B1 (en) |
JP (1) | JP2002030910A (en) |
KR (1) | KR20020048939A (en) |
CN (1) | CN1203247C (en) |
DE (1) | DE60118930T2 (en) |
WO (1) | WO2002008578A1 (en) |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9750425B2 (en) | 2004-03-23 | 2017-09-05 | Dune Medical Devices Ltd. | Graphical user interfaces (GUI), methods and apparatus for data presentation |
JP4935198B2 (en) * | 2006-06-09 | 2012-05-23 | トヨタ自動車株式会社 | Control device for variable valve mechanism |
JP4550912B2 (en) * | 2008-03-13 | 2010-09-22 | ジヤトコ株式会社 | Solenoid valve control device |
US8136616B2 (en) * | 2008-11-17 | 2012-03-20 | Ford Global Technologies, Llc | Oil control valve degradation detection and cleaning strategy |
CN103899374A (en) * | 2014-03-27 | 2014-07-02 | 哈尔滨工程大学 | Mechanical device capable of infinitely adjusting phase advance angle |
JP6133820B2 (en) | 2014-06-27 | 2017-05-24 | トヨタ自動車株式会社 | Hydraulic control valve control device |
JP2016023620A (en) * | 2014-07-23 | 2016-02-08 | トヨタ自動車株式会社 | Internal combustion engine control unit |
US11002166B2 (en) | 2019-05-17 | 2021-05-11 | Ford Global Technologies, Llc | Methods and systems for an active exhaust valve |
JP7167224B2 (en) * | 2021-03-19 | 2022-11-08 | 日立建機株式会社 | working machine |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS543B2 (en) * | 1974-02-28 | 1979-01-05 | ||
CA1331547C (en) * | 1988-08-01 | 1994-08-23 | Yukihiro Matsumoto | Valve operating system for internal combustion engine |
JP3094762B2 (en) | 1993-12-24 | 2000-10-03 | 日産自動車株式会社 | Variable valve train for internal combustion engine |
JP3098676B2 (en) | 1994-07-13 | 2000-10-16 | トヨタ自動車株式会社 | Valve timing control device for internal combustion engine |
JP3998735B2 (en) | 1996-01-11 | 2007-10-31 | 株式会社デンソー | Valve timing adjusting device for internal combustion engine |
JPH09195808A (en) * | 1996-01-19 | 1997-07-29 | Toyota Motor Corp | Controller for engine and automatic transmission |
JP3546651B2 (en) * | 1997-07-30 | 2004-07-28 | トヨタ自動車株式会社 | Abnormality detection device for valve timing control device |
DE19745908B4 (en) | 1997-10-17 | 2004-03-04 | Ina-Schaeffler Kg | Device for changing the control times of gas exchange valves of an internal combustion engine, the device being designed as a vane adjustment device |
JP3815014B2 (en) | 1997-12-24 | 2006-08-30 | アイシン精機株式会社 | Valve timing control device |
JP2000303864A (en) * | 1999-04-21 | 2000-10-31 | Toyota Motor Corp | Abnormality processor for valve characteristic variable device |
JP3945117B2 (en) | 2000-03-09 | 2007-07-18 | トヨタ自動車株式会社 | Valve characteristic control device for internal combustion engine |
-
2000
- 2000-07-21 JP JP2000220391A patent/JP2002030910A/en active Pending
-
2001
- 2001-06-28 EP EP01945701A patent/EP1301691B1/en not_active Expired - Lifetime
- 2001-06-28 WO PCT/JP2001/005619 patent/WO2002008578A1/en active IP Right Grant
- 2001-06-28 DE DE60118930T patent/DE60118930T2/en not_active Expired - Fee Related
- 2001-06-28 KR KR1020027003651A patent/KR20020048939A/en not_active Application Discontinuation
- 2001-06-28 CN CNB018021352A patent/CN1203247C/en not_active Expired - Fee Related
- 2001-06-28 US US10/088,472 patent/US6615779B2/en not_active Expired - Fee Related
Non-Patent Citations (1)
Title |
---|
See references of WO0208578A1 * |
Also Published As
Publication number | Publication date |
---|---|
US6615779B2 (en) | 2003-09-09 |
DE60118930T2 (en) | 2006-09-14 |
EP1301691B1 (en) | 2006-04-19 |
WO2002008578A1 (en) | 2002-01-31 |
CN1386158A (en) | 2002-12-18 |
CN1203247C (en) | 2005-05-25 |
JP2002030910A (en) | 2002-01-31 |
US20020134335A1 (en) | 2002-09-26 |
KR20020048939A (en) | 2002-06-24 |
DE60118930D1 (en) | 2006-05-24 |
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